GB2239963A - Injection timing control apparatus for distributor type fuel injection pumps - Google Patents
Injection timing control apparatus for distributor type fuel injection pumps Download PDFInfo
- Publication number
- GB2239963A GB2239963A GB9024782A GB9024782A GB2239963A GB 2239963 A GB2239963 A GB 2239963A GB 9024782 A GB9024782 A GB 9024782A GB 9024782 A GB9024782 A GB 9024782A GB 2239963 A GB2239963 A GB 2239963A
- Authority
- GB
- United Kingdom
- Prior art keywords
- timer
- servo valve
- type fuel
- fuel injection
- control apparatus
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
- F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
- F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
- F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
- F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
- F02M41/128—Varying injection timing by angular adjustment of the face-cam or the rollers support
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
- F02D1/16—Adjustment of injection timing
- F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
- F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- High-Pressure Fuel Injection Pump Control (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
An injection timing control apparatus for a distributor type fuel injection pump comprises a timer piston 53 associated with a roller holder lever 6 which moves in response to the pressure in the timer high-pressure chamber 54. A servo valve 58 slidably provided in the timer piston 53 is arranged on the timer high-pressure chamber side of the roller holder lever. The valve 58 is guided in a bush 57 mounted in the piston 53 and is controlled either by fuel pressure in the pump 3 or by a solenoid. <IMAGE>
Description
INJECTION TIMING CONTROL APPARATUS FOR DISTRIBUTOR TYPE FUEL INJECTION
PUMPS
BACKGROUND OF THE INVENTION Field of the Invention
The present invention relates to an injection timing control apparatus for di9tributor type fuel injection pumps, particularly to an injection timing control apparatus for distributor type fuel injection pump which uses a servo valve.
Description of the Prior Art
With conventional fuel injection pumps, an increase in engine speed has to be matched by an advance in the fuel injection timing to ensure that the fuel is injected with the optimum timing. For this, the fuel injection pump is equipped with a fuel injection timing control device (timer).
Usually a pressure control valve is used to produce a rise in the pressure in the pump chamber corresponding to the increase in the engine speed, and the injection timing is controlled by controlling the timer, using this pump chamber pressure as the pressure source.
There are timers which are provided with servo valve arrangements. In the injection timing adjustment apparatus for a distributor type fuel injection pump according to Japanese Patent Laid-open Application 5832928/1983, for example, to prevent the torque reaction from the plunger cam disk setting up vibration in the 2 roller, a servo valve is used to temporarily break the connection between the pump chamber and the timer highpressure chamber, creating a hydraulic lock.
An injection timing adjustment apparatus for a distributor type fuel injection pump will now be briefly described, with reference to Figure 7. Figure 7 is a longitudinal cross-sectional view -of a conventional injection timing adjustment apparatus 1 for a distributor type fuel injection pump. A roller holder 4 is arranged in a pump chamber 3 formed in a pump housing 2. A roller 5 is rotatably held by the roller holder 4, and abuts the cam disk of a plunger (not shown) which is mounted in the pump housing 2. A drive shaft (not shown) drives the plunger in a reciprocating rotational motion to intake and inject the fuel.
A lever 6 is af fixed to the roller holder 4. The contact between the roller 5 and the cam disk can be altered by adjusting the angle of the lever 6 to change the range of the operating cam surface and thereby control the fuel injection timing.
The end of the lever 6 contacts a timer piston 8 via a slide roller 7. This timer piston 8 is capable of reciprocating motion in a timer cylinder 9 formed in the pump housing 2. One end of the timer cylinder 9 is sealed shut by a lid member 10 and an O-ring 11, forming a timer high- pressure chamber 12 between the timer piston 8 and the lid member 10. The other end of the timer cylinder 9 is also sealed by a lid member 13 and a O-ring 14, forming a 1 3 timer low-pressure chamber. The timer low-pressure chamber is connected to a low-pressure section at the intake side of the fuel feed pump (not shown).
A timer piston play damper spring 16 is provided between the lid member 13 and the timer piston 8 which together with a servo valve control spring 19, described below, urges the timer piston 8 towArds the timer high pressure chamber 12.
A guide bush 17 is af fixed in the timer piston 8.
The guide bush 17 contains a servo valve 18 which can be moved to the left and right, with respect to the drawing.
A servo valve control spring 19 is provided between the servo valve 18 and the lid member 13.
Formed in the timer piston 8 is a high-pressure hydraulic passage 20 which communicates to the timer high pressure chamber 12. In the guide bush 17 are formed an inflow high-pressure aperture 21 that communicates with the pump chamber 3, and a communicating aperture 22 that communicates with the high-pressure hydraulic passage 20.
Formed in the servo valve 18 is a low-pressure-side communicating passage 23 which can be connected to the communicating aperture 22 and to the timer low-pressure chamber 15.
In Figure 7 the injection timing adjustment apparatus I for a distributor type fuel injection pump thus configured is shown in the maximum retard state, in which the rise in pressure in the pump chamber 3 is exerted on the servo valve 18 via the high-pressure aperture 21, - 4 moving the servo valve 18 to the right against the f orce of the servo valve control spring 19 and bringing the highpressure aperture 21 into communication with the communicating aperture 22. As a result, the high pressure in the pump chamber 3 extends, via the high-pressure hydraulic passage 20, to the timer high-pressure chamber 12, also moving the timer piston 8 -to the right. This causes the lever 6 to rotate counterclockwise, which changes the range of contact between the roller 5 and the face of the cam disk, enabling the timing to be advanced. This position is stabilized when the movement of the timer piston 8 to the right breaks the communication between the high-pressure aperture 21 and the communicating aperture 22.
A pressure drop in the pump chamber 3 will cause the servo valve 18 to be moved to the left by the force of the servo valve control spring 19. This brings the communicating aperture 22 into communication with the highpressure hydraulic passage 20, allowing fluid under high pressure in the timer high-pressure chamber to flow into the timer low-prelssure chamber 15. This moves the timer piston 8 to the left and rotates the lever 6 clockwise, retarding the timing. This conventional servo valve timer, that is, the injection timing adjustment apparatus 1 for a distributor type fuel injection pump, features good response com pared with a standard timer that does not have a servo valve 18, and other merits include low hysteresis and the small effect that advancing the timing has on Z changes in the fuel injection amount. on the other hand, as the servo valve 18 is located on the timer low-pressure chamber 15 side of the lever 6, assuming that the direction of rotation of the engine, i. e. of the cam disk and the plunger is the same, a servo valve 18 cannot be provided in cases where the engine is located on the timer low-pressure chamber 15 side as the engine cylinder block would be in the way. Thus, the servo valve arrangement is only applicable to a limited number of engine types.
This problem is not limited to the abovedescribed injection timing control apparatus 1 in which the servo valve 18 is driven by the hydraulic pressure in the pump chamber 3, but also arises in the case of injection timing control apparatuses that use solenoids and the like. This is explained in the following, in which parts which are the same as those in Figure 7 have the same reference numerals.
Figure 8 shows an injection timing adjustment apparatus 30 in which a servo valve 33 is screwed into a rod 32 of an actuator such as linear solenoid 31 and is provided with an actuator play damper spring 34. In addition, a timer piston play damper spring 35 is provided between the timer piston 8 and the linear solenoid 31.
A high-pressure hydraulic passage 36 is formed in the timer piston 8, a high-pressure hydraulic passage 38 in the guide bush 37 and an annular groove 39 in the servo valve 33. In addition, provided in the servo valve 33 are a center low-pressure hydraulic passage 40 which 6 communicates with the annular groove 39, and a radial lowpressure hydraulic passage 41 which communicates with the center low-pressure hydraulic passage 40.
In this arrangement, when the servo valve 33 is moved to the right by the linear solenoid 31 the pump chamber 3 is brought into communication with the timer high-pressure chamber 12 via the high-pressure hydraulic passage 36, the high-pressure hydraulic passage 38, the annular groove 39, the communicating aperture 22 and the high-pressure hydraulic passage 20, whereby the timer piston 8 is moved to the right by the pump chamber pressure, advancing the timing.
Conversely, when the servo valve 33 is moved to the left by the linear solenoid 31, the timer high-pressure chamber 12 is brought into communication with the timer low-pressure chamber 15 via the highpressure hydraulic passage 20, the center low-pressure hydraulic passage 40 and the radial low-pressure hydraulic passage 41, moving the timer piston 8 to the left and retarding the timing.
The merits of this type of injection timing adjustment apparatus 30 include structural simplicity, good precision, and good resistance to interference from the drive reaction (torque reaction). However, as in the case of the injection timing adjustment apparatus 1 described above, the servo valve 33 and the linear solenoid 31 are located on the timer low-pressure chamber 15 side of the lever 6, with the linear solenoid 31 protruding quite considerably, making it impossible to avoid interference i 7 with the engine.
An object of the present invention therefore is to provide an injection timing control apparatus for a distributor type fuel injection pump which enables the advantages of the servo valve arrangement to be utilized by being provided with the ability to accommodate engines arrangements in which parts of the engine are on the timer low-pressure chamber side.
This object is attained by the injection timing control apparatus for a distributor type fuel injection pump according to the present invention comprising a timer piston which is associated with the roller holder lever and moves in response to the pressure in the timer highpressure chamber, and a servo valve slidably provided in the timer piston, wherein the servo valve is arranged on the timer high-pressure chamber side of the roller holder lever.
In the case of an injection timing control apparatus which utilizes the pressure in the pump chamber for the operation and positioning of the servo valve, the apparatus is configured so that even if the servo valve control pressure chamber which routes the pump pressure chamber is arranged on the timer high-pressure chamber side, it does not communicate with the timer high-pressure chamber.
Moreover, in the case of an injection timing adjustment apparatus utilizing a solenoid means or the like, the solenoid means is provided on the timer high- 8 pressure chamber side.
With the injection timing control apparatus for a distributor type fuel injection pump according to the present invention, unlike in the conventional arrangement, the servo valve is not provided on the timer low-pressure chamber side of the lever but on the timer high-pressure chamber side, enabling external projections on the timer low-pressure chamber side to be minimized, making this an apparatus that can be flexibly adaptable to the positional arrangement of the engine and can utilize the advantages of the servo valve arrangement.
Further features of the invention, its nature and various advantages will be more apparent from the accompanying drawings and following detailed description of embodiments of the invention.
BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 is a longitudinal cross-section drawing of an injection timing control apparatus for a distributor type fuel injection pump according to a first embodiment of the present invention; Figure 2 is a magnified cross-sectional view of the principal parts of the first embodiment when the timing is advanced; Figure 3 is a magnified cross-sectional view of the principal parts of the first embodiment when the timing is retarded; Figure 4 is a longitudinal cross-section drawing of an injection timing control apparatus for a distributor 1 9 type fuel injection pump according to a second embodiment of the invention; Figure 5 is a magnified cross-sectional view of the principal parts of the first embodiment when the timing is advanced; Figure 6 is a magnified cross-sectional view of the principal parts of the f irst emboMment when the timing is retarded; Figure 7 is a longitudinal cross-section drawing of a conventional injection timing adjustment apparatus for a distributor type fuel injection pump; and Figure 8 is a longitudinal cross-section drawing of another conventional injection timing adjustment apparatus.
DETAILED DESCRIPTION OF THE INVENTION
A first embodiment of the present invention will now be described with reference to Figures 1 to 3. Figure 1 is a longitudinal cross-section drawing of an injection timing control apparatus 50 for a distributor type fuel injection pump and Figures 2 and 3 are magnified crosssectional views of the principal parts of the first embodiment, the former when the timing is advanced and the latter when the timing is retarded.
A timer cylinder 9 is formed between lid members 51 and 52. Provided in the timer cylinder 9 is a timer piston 53 which can slide back and forth. The space between the timer piston 53 and the lid member 51 forms a timer high-pressure chamber 54, and the space between the - 10 timer piston 53 and the other lid member 52 forms a timer low- pressure chamber 55. A servo valve control pressure chamber body 56 affixed in the timer high-pressure chamber 54 and an opposed guide bush - 57 provided in the timer piston 53 contain a servo valve 58 which can slide back and forth.
Formed between the servo valve 58 and the servo valve control pressure chamber body 56 is a servo valve control pressure chamber 59 into which high-pressure fluid is brought from the pump chamber 3. For this, a highpressure hydraulic passage 60 is formed in the timer piston 53, an intake port 61 in the guide bush 57, and a radial communicating passage 62 and a center communicating passage 63 in the servo valve 58, and this center communicating passage 63 communicates with the servo valve control pressure chamber 59.
In addition, the guide bush 57 has a communicating port 64 and a communicating groove 65 which opens into the timer high-pressure chamber 54. The space between the guide bush 57 and the servo valve 58 f orms a low-pressure-side -communicating chamber 66. An intake port 67 f ormed in the guide bush 57 and a low-pressure-side passage 68 in the timer piston 53 enables the low-pressureside communicating chamber 66 to be connected to the timer low-pressure chamber 55.
A timer piston play damper spring 69 is provided between the timer piston 53 and the lid member 52, and a servo valve control spring 71 is provided between the servo 11 valve 58 and a spring seat 70 that is supported by the lid member 51.
In the injection timing control apparatus for a distributor type fuel injection pump 50 thus configured, when there is a rise in the fuel pressure in the pump chamber 3, this fuel pressure is communicated via the highpressure hydraulic passage 60, the-intake port 61, the radial communicating passage 62 and the center communicating passage 63 to the servo valve control pressure chamber 59, to thereby move the servo valve 58 to the right. This brings the pump chamber 3 into communication with the timer high-pressure chamber 54 via the radial communicating passage 62, communicating port 64 and communicating groove 65, and the movement of the timer piston 53 to the right turns the lever 6 counterclockwise, advancing the timing, and stability is reached when the communicating port 64 is closed.
Conversely, as shown in Figure 3, when there is a drop in the fuel pressure in the pump chamber 3 the servo valve 58 is moved to the left by the f orce of the servo valve control spring 71 and there is an outf low of fuel f rom the servo valve control pressure chamber 59. As a result, the timer high-pressure chamber 54 is brought into communication with the timer low-pressure chamber 55 via the communicating groove 65, the communicating port 64, the low-pressure-side communicating chamber 66, the intake port 67 and the low-pressure-side passage 68, and the movement of the timer piston 53 to the left turns the lever 6 12 clockwise, retarding the timing.
The function of the servo valve 58 can thus be utilized, and the servo valve 58 itself can be positioned on the timer high-pressure chamber 54 side of the lever 6, avoiding interference with the lid member 52 on the timer low-pressure chamber 55 side.
Moreover, there is in fact rittle need to provide the timer piston play damper spring 69, and even when a spring is used it can be made very short. This means that the lid member 52 on the timer low-pressure chamber 55 side protrudes much less than in a conventional arrangement, so there are no design problems even when parts of the engine are located on the timer low-pressure chamber 55 side. This enables the range of application of the invention to be broadened and the advantages of the servo valve system utilized to good effect, including with respect to exhaust gas emission controls.
Furthermore, compared with conventional servo valve timers there is a large degree of freedom concerning the outer diameter of the servo valve control spring, and this degree of freedom can be increased. It is also possible to readily develop the arrangement into a twostage spring timer.
A second embodiment of the present invention will now be described with reference to Figures 4 to 6. Figure 4 is a longitudinal cross-section drawing of an injection timing control apparatus 80 for a distributor type fuel injection pump and Figures 5 and 6 are magnified cross- 13 sectional views of the principal parts of the second embodiment, the former when the timing is advanced and the latter when the timing is retarded.
In the injection timing control apparatus 80, an annular groove 82 is formed in a servo valve 81. A linear solenoid 83, for example, is used to constitute an actuator which is used to impart reciprocal -motion to the servo valve 81.
The provision of the linear solenoid 83 on the timer high-pressure chamber 54 side of the lever 6 and other such structural details are substantially the same as those of the injection timing control apparatus 50, and further explanation thereof is therefore omitted here. Reference numeral 84 denotes a linear solenoid play damper spring.
As shown in Figure 5, in the case of the injection timing control apparatus 80 the timing is advanced by using the linear solenoid 83 to move the servo valve 81 to the right, which brings the timer highpressure chamber 54 into communication with the pump chamber 3, via the communicating groove 65, the communicating port 64, the annular groove 82, the intake port 61 and the high-pressure hydraulic passage 60. High pressure in the pump chamber 3 acting on the timer high-pressure chamber 54 moves the timer piston 53 to the right, turning the lever 6 counterclockwise.
Conversely, retardation (Figure 6) is effected by the servo valve 81 being moved to the left by the linear 14 solenoid 83. This brings the timer high-pressure chamber 54 into communication with the timer low-pressure chamber 55 via the communicating groove 65, the communicating port 64, the low-pressure-side communicating chamber 66, the intake port 67 and the low-pressure-side passage 68. As a result the timer piston 53 is moved to the left and the lever 6 is turned clockwise.
Like the injection timing control apparatus 50, the servo valve 81 of the injection timing control apparatus 80 is arranged on the timer highpressure chamber 54 side of the lever 6, and it is therefore possible to adapt the invention to engines with parts located on the servo valve 58 side.
Also, the servo valve 81 which constitutes the control rod portion of the linear solenoid 83 only has to be provided with the annular groove 82, simplifying the structure. Moreover, as the pump housing 2 and other components are the same as the ones used in mechanical injection pumps, if it is desired to implement electronic control for just the injection timing, this can be readily realized merely by replacing the linear solenoid 83 and the servo valve 81.
i
Claims (23)
1. An injection timing control apparatus for a distributor type fuel injection pump comprising:
a timer piston which is associated with a roller holder lever and moves in response to the pressure in a timer high-pressure chamber; and a servo valve slidably piovided in the timer piston; wherein the servo valve is arranged on the timer high-pressure chamber side of the roller holder lever.
2. An injection timing control apparatus for a distributed type fuel injection pump according to claim 1 further comprising a roller provided on the roller holder which contacts a cam disk of a plunger that injects the fuel and wherein the timer piston is located between the timer highpressure chamber and the timer low-pressure chamber and the timing is advanced by moving the timer piston toward the side with the timer lowpressure chamber.
3. An injection timing control apparatus for a distributed type fuel injection pump according to claim 2 in which the timer piston is moved toward the side with the timer low-pressure chamber by moving the servo valve away from the timer high-pressure chamber side and toward the timer low-pressure chamber side, and the timer piston is moved toward the side with the timer high-pressure chamber by moving the servo valve away from the timer low-pressure chamber and toward the side with the timer highpressure chamber.
16
4. An injection timing control apparatus for a distributed type fuel injection pump according to claim 3 in which the pressure in the distributed type fuel injection pump chamber is employed as the motive force to move the servo valve.
5. An injection timing control apparatus for a distributed type fuel injection pump-according to claim 4 further comprising means for guiding the servo- valve movement comprising a guide bush affixed in the timer piston and a servo valve control pressure chamber body provided in the timer high-pressure chamber.
6. An injection timing control apparatus for a distributed type fuel injection pump according to claim 5 in which the space between the servo valve control pressure chamber body and the servo valve constitutes a servo valve control pressure chamber.
7. An injection timing control apparatus for a distributed type fuel injection pump according to claim 6 further comprising a first communicating passage constituted by the space between the servo valve control pressure chamber and the pump chamber.
S. An injection timing control apparatus for a distributed type fuel injection pump according to claim 7 in which the first communicating passage is constituted by a high-pressure hydraulic passage formed in the timer piston, an intake port formed in the guide bush and a radial communicating passage and a center communicating passage formed in the servo valve.
17
9. An injection timing control apparatus for a distributed type fuel injection pump according to claim 5 further comprising a servo valve control spring which urges the servo valve against the force of the pump chamber pressure.
10. An injection timing control apparatus for a distributed type fuel injection pump_according to claim 6 further comprising a second communicating passage which enables the timer high-pressure chamber and the pump chamber to be brought into communication when the servo valve is moved away from the timer high-pressure chamber side and toward the timer low-pressure chamber side.
11. An injection timing control apparatus for a distributed type fuel injection pump according to claim 10 in which the second communicating passage is constituted by a high-pressure hydraulic passage formed in the timer piston, an intake port formed in the guide bush, a radial communicating passage formed in the servo valve, and a communicating port and a communicating groove formed in the guide bush.
12. An injection timing control apparatus for a distributed type fuel injection pump according to claim 5 in which the space between the guide bush and the servo valve constitutes a low-pressure-side communicating chamber.
13. An injection timing control apparatus for a distributed type fuel injection pump according to claim 12 further comprising a third communicating passage which 18 enables the timer high-pressure chamber and the timer lowpressure chamber to be brought into communication via the low-pressure-side communicating chamber when the servo valve is moved away from the timer low-pressure chamber side and toward the timer high-pressure chamber side.
14. An injection timing control appara tus for a distributed type fuel injection pump according to claim 13 in which the third communicating passage is constituted by a communicating port and communicating groove formed in the guide bush, an intake port formed in the guide bush, and a low-pressure-side communicating passage formed in the timer piston.
15. An injection timing control apparatus for a distributed type fuel injection pump according to claim 3 in which a linear solenoid is employed as the motive force to move the servo valve.
16. An injection timing control apparatus for a distributed type fuel injection pump according to claim 15 further comprising means for guiding the servo valve movement comprising a guide bush affixed in the timer piston.
17. An injection timing control apparatus for a distributed type fuel injection pump according to claim 15 in which the linear solenoid holding the servo valve is arranged on the opposite side to the roller holder lever.
18. An injection timing control apparatus for a distributed type fuel injection pump according to claim 16 further comprising a fourth communicating passage which 19 enables the timer high-pressure chamber and the pump chamber to be brought into communication when the servo valve is moved away from the timer high-pressure chamber side and toward the timer low-pressure chamber side.
19. An injection timing control apparatus for a distributed type fuel injection pump according to claim 18 in which the fourth communicating passage is constituted by a high-pressure hydraulic passage formed in the timer piston, an intake port formed in the guide bush, an annular groove formed in the servo valve and a communicating port and communicating groove formed in the guide bush.
20. An injection timing control apparatus for a distributed type fuel injection pump according to claim 16 in which the space between the guide bush and the servo valve constitutes a low-pressure-side communicating chamber.
21. An injection timing control apparatus for a distributed type fuel injection pump according to claim 20 further comprising a third communicating passage which enables the timer high-pressure chamber and the timer lowpressure chamber to be brought into communication via the low-pressure-side communicating chamber when the servo valve is moved away from the timer low-pressure chamber side and toward the timer highpressure chamber side.
22. An injection timing control apparatus for a distributed type fuel injection pump according to claim 21 in which the third communicating passage is constituted by a communicating port and communicating groove formed in the guide bush, an intake port formed in the guide bush, and a low-pressure- side communicating passage formed in the timer piston.
23. An injection timing control apparatus for a distributor type fuel injection pump substantially as herein described with reference to Figures 1 to 6 of the accompanying drawings.
Published 1991 at7be Patent Office. State House. 66/71 High Holborn. IA)ndonWCIR41?. Further copier. may be obtained from Sales Branch. Unit 6, Nine Mile PbinL Cwmfehnfach. Cross Keys. Newport. NPI 7HZ. Printed by Multiplex techniques lid. St Mary Cray. Kent.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1327154A JPH03188427A (en) | 1989-12-19 | 1989-12-19 | Injection timing controlling for distribution type fuel injection pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB9024782D0 GB9024782D0 (en) | 1991-01-02 |
| GB2239963A true GB2239963A (en) | 1991-07-17 |
Family
ID=18195915
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB9024782A Withdrawn GB2239963A (en) | 1989-12-19 | 1990-11-14 | Injection timing control apparatus for distributor type fuel injection pumps |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US5125802A (en) |
| JP (1) | JPH03188427A (en) |
| GB (1) | GB2239963A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2700187A1 (en) * | 1993-01-02 | 1994-07-08 | Bosch Gmbh Robert | Fuel injection pump for internal combustion engines. |
| WO1995019498A1 (en) * | 1994-01-15 | 1995-07-20 | Lucas Industries Public Limited Company | Fuel pumping apparatus |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0635100A1 (en) * | 1992-04-09 | 1995-01-25 | Lucas Industries Public Limited Company | Fuel pumping apparatus |
| JP3560711B2 (en) * | 1995-04-07 | 2004-09-02 | 株式会社日本自動車部品総合研究所 | Injection timing control device for fuel injection pump |
| DE19533807A1 (en) * | 1995-09-13 | 1997-03-20 | Bosch Gmbh Robert | Fuel injection pump |
| DE19849925A1 (en) * | 1998-10-29 | 2000-05-04 | Bosch Gmbh Robert | Fuel injection pump |
| DE19854766A1 (en) * | 1998-11-27 | 2000-05-31 | Bosch Gmbh Robert | Fuel injection pump |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB925979A (en) * | 1960-08-30 | 1963-05-15 | Cav Ltd | Liquid fuel injection pumps |
| GB948979A (en) * | 1961-12-07 | 1964-02-05 | Cav Ltd | Liquid fuel pumps |
| GB984745A (en) * | 1962-07-11 | 1965-03-03 | Cav Ltd | Liquid fuel pumps for supplying fuel to internal combustion engines |
| GB1461573A (en) * | 1973-04-14 | 1977-01-13 | Cav Ltd | Fuel injection pumping apparatus |
| GB1523429A (en) * | 1976-05-21 | 1978-08-31 | Stanadyne Inc | Timing control for fuel injection pump |
| GB2046351A (en) * | 1979-03-10 | 1980-11-12 | Bosch Gmbh Robert | A fuel injection pump for an internal combustion engine |
| GB2050647A (en) * | 1979-05-01 | 1981-01-07 | Nissan Motor | Fuel injection pump with automatic injection advance |
| US4557240A (en) * | 1984-05-09 | 1985-12-10 | Diesel Kiki Co., Ltd. | Injection timing control device for distributor-type fuel injection pumps |
| US4563996A (en) * | 1983-10-11 | 1986-01-14 | Robert Bosch Gmbh | Fuel injection pump for internal combustion engines |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1238283A (en) * | 1967-09-22 | 1971-07-07 | ||
| JPS551418A (en) * | 1978-06-16 | 1980-01-08 | Diesel Kiki Co Ltd | Injection timing device for distribution-type fuel injection pump |
| US4224916A (en) * | 1978-11-13 | 1980-09-30 | Stanadyne, Inc. | Timing control for fuel injection pump |
| US4329961A (en) * | 1980-09-29 | 1982-05-18 | General Motors Corporation | Diesel injection pump timing control with electronic adjustment |
| JPS5786533A (en) * | 1980-11-15 | 1982-05-29 | Diesel Kiki Co Ltd | Regulating device of injection timing in distributor type fuel injection pump |
| US4476837A (en) * | 1982-12-07 | 1984-10-16 | Stanadyne, Inc. | Method and system for fuel injection timing |
| US4526154A (en) * | 1982-12-27 | 1985-07-02 | Ambac Industries, Incorporated | Timing control mechanism for a fuel injection pump |
| JPS6141840U (en) * | 1984-06-12 | 1986-03-17 | 株式会社ボッシュオートモーティブ システム | Injection timing adjustment device for distributed fuel injection pump |
| DE3512019A1 (en) * | 1985-04-02 | 1986-10-02 | Robert Bosch Gmbh, 7000 Stuttgart | FUEL INJECTION PUMP |
-
1989
- 1989-12-19 JP JP1327154A patent/JPH03188427A/en active Pending
-
1990
- 1990-11-14 GB GB9024782A patent/GB2239963A/en not_active Withdrawn
- 1990-11-19 US US07/615,347 patent/US5125802A/en not_active Expired - Fee Related
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB925979A (en) * | 1960-08-30 | 1963-05-15 | Cav Ltd | Liquid fuel injection pumps |
| GB948979A (en) * | 1961-12-07 | 1964-02-05 | Cav Ltd | Liquid fuel pumps |
| GB984745A (en) * | 1962-07-11 | 1965-03-03 | Cav Ltd | Liquid fuel pumps for supplying fuel to internal combustion engines |
| GB1461573A (en) * | 1973-04-14 | 1977-01-13 | Cav Ltd | Fuel injection pumping apparatus |
| GB1523429A (en) * | 1976-05-21 | 1978-08-31 | Stanadyne Inc | Timing control for fuel injection pump |
| GB2046351A (en) * | 1979-03-10 | 1980-11-12 | Bosch Gmbh Robert | A fuel injection pump for an internal combustion engine |
| GB2050647A (en) * | 1979-05-01 | 1981-01-07 | Nissan Motor | Fuel injection pump with automatic injection advance |
| US4563996A (en) * | 1983-10-11 | 1986-01-14 | Robert Bosch Gmbh | Fuel injection pump for internal combustion engines |
| US4557240A (en) * | 1984-05-09 | 1985-12-10 | Diesel Kiki Co., Ltd. | Injection timing control device for distributor-type fuel injection pumps |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2700187A1 (en) * | 1993-01-02 | 1994-07-08 | Bosch Gmbh Robert | Fuel injection pump for internal combustion engines. |
| WO1995019498A1 (en) * | 1994-01-15 | 1995-07-20 | Lucas Industries Public Limited Company | Fuel pumping apparatus |
| US5651348A (en) * | 1994-01-15 | 1997-07-29 | Lucas Industries Public Limited Company | Fuel pumping apparatus |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH03188427A (en) | 1991-08-16 |
| GB9024782D0 (en) | 1991-01-02 |
| US5125802A (en) | 1992-06-30 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |